Speed/torque enhancing power transmission

ABSTRACT

A speed/torque enhancing power transmission is disclosed that translates slow rotating, high torque motion to high rotation, low torque motion or alternatively high rotating low torque motion to low rotating high torque motion and is suitable as a speed increaser for use in a device like a wind turbine. As a speed increaser the transmission has certain advantages, such as reduced weight and/or size compared to other units having the same performance characteristics. The speed increaser employs a pair of externally toothed spur gears orbiting in a non-rotating manner 180° out of phase inside an internally toothed ring gear. The input drives the ring gear and the orbiting spur gears drive separate eccentrics on the output shaft extending in opposite directions to provide dual output. In one embodiment, cross guide projections on the spur gear and cross guide projections on the housing engage slots in a swash plate.

This application claims priority to PCT Application No.PCT/US2010/051046, filed Oct. 1, 2010, and is also aContinuation-in-Part of U.S. Utility application Ser. No. 12/572,672,filed Oct. 2, 2009, by Michael E. Winiasz, which claims priority to U.S.Provisional Patent Application Ser. No. 61/103,424, filed Oct. 7, 2008.

BACKGROUND

The present disclosure relates to a speed/torque increaser or enhancerthat is suitable for use on motors and/or turbines, such as a windturbine, for converting slow rotating, high torque motion into highrotation, low torque motion. The present disclosure can also bedescribed as a planocentric gearbox.

Presently, gear boxes for wind turbine applications are complexmulti-stage gearing arrangements which are not only bulky and heavy butquite difficult to service when installed on the wind turbine tower. Forexample, a presently available 600 kilowatt commercially available windturbine gear box weighs about 8,600 pounds or approximately 77 watts perpound.

It has thus been desired to provide a way or means of reducing thecomplexity, size and weight of a gear box for substantially increasingthe speed/torque of an output shaft and particularly for wind turbinegenerator applications.

BRIEF DESCRIPTION

Disclosed in embodiments are gearboxes that provide large increases inshaft rotational speed or alternatively torque in an efficient manner. Agearing arrangement is provided in a housing and is capable of beingmounted to a source of input power, such as a motor, turbine, or otherprime mover. Such speed/torque increasers are useful for enabling largeincreases in shaft rotational speed in a small volume of space oralternatively torque when employed as a speed reducer and which can beuseful as a speed increaser in machines such as wind turbines. Thetransmission employed as a speed increaser disclosed achieves a masspower density of 250 Watts per pound (550 watts per kilogram) and avolume power density of 23 watts per cubic centimeter.

In some embodiments, the transmission, employed as a speed increasercomprises a housing, an input shaft, an internal spur gear, an externalspur gear, a top plate, a cross plate, an eccentric ring, and an outputshaft. The housing has a first end and a second end. The rotatable inputshaft extends through the first end and including a plate mounted on oneend. The internal spur gear is mounted on the plate. An external spurgear engages the internal spur gear and has a first pair of cross guidepins projecting therefrom towards the second end of the housing. The topplate is located at the second end of the housing and has a second pairof cross guide pins projecting therefrom towards the first end of thehousing. The cross plate is located between the top plate and theexternal spur gear and has a first pair of slots adapted to receive thefirst pair of cross guide pins and a second pair of slots adapted toreceive the second pair of cross guide pins, both pairs of pins beingmovable within the slots. The eccentric ring is mounted along therotational axis of the external spur gear. The rotatable output shaftextends through the top plate and the cross plate, and engages theeccentric ring.

In other embodiments, the speed increaser comprises a geared bearing, aninner gear, an output shaft, a swash plate, and a back plate. The gearedbearing contains teeth on an internal face and can be attached to a hubplate. The inner gear contains teeth on an external face and ispositioned to contact the teeth of the geared bearing. The inner gearhas a bore and a first pair of drive dogs attached to a front face. Theoutput shaft is positioned within the inner gear bore and is coaxialwith the geared bearing. The swash plate contains a first pair of slotsand a second pair of slots. The back plate has a second pair of drivedogs attached to a rear face. The first pair of drive dogs mates withthe first pair of slots and the second pair of drive dogs mates with thesecond pair of slots.

In another embodiment or version of the disclosure, a speed increaserhas an input member or shaft attached to an internally toothed ring gearwhich is journalled for rotation on a housing having an output shaftjournalled for rotation thereon. The output shaft has an eccentric uponwhich is journalled an externally toothed spur gear having the pitchdiameter of the teeth slightly less than the pitch diameter of the ringgear teeth with the spur gear contacting the teeth of the ring gear inorbiting non-rotating contact. The housing has a first pair of slotsformed therein; and, the spur gear has a second pair of slots formedtherein. A swash plate has a first pair of cross guide projections inthe form of dogs or lugs on one side thereof and a second pair of crossguide projections in the form of dogs or lugs on the opposite or facethereof with the first set of dogs engaging the first set of slots inthe housing and the second set of dogs engaging the second set of slotsin the spur gear.

In yet another embodiment or version, the swash plate has hardenedremovable plates provided on the first and second set of dogs and on thesurface of the swash plate for providing ready replacement of thesliding surfaces.

In another version or embodiment, the swash plate dogs are cross drilledfor communicating with grooves in wear plates mounted on the dogs forproviding lubricant galleries to feed lubricant to recesses formed inthe wear plates. A lubricant supply port provided in the housingcommunicates with cross ports for supplying lubricant to the wearplates.

In another version or embodiment, the speed increaser has a generatorstator and rotor mounted within the speed increaser housing with thestator mounted on the housing and generator rotor attached to the outputshaft and thus the generator is positioned within the housing for thespeed increaser. In another version, the input shaft or member has thehub of a fluid turbine impeller attached thereto and the hub extendsover the housing of the speed increaser and generator forming anintegral assembly.

In another version, the output shaft extends to have an end journalledwithin the impeller hub; and, the shaft may be a hollow tubular memberfor permitting power leads to pass through the shaft to the impeller hubfor installations where the impeller hub is of the type containing servomotors for varying the pitch of the impeller blades.

In another version of the transmission employed as speed increaser,multiple output shafts are operated by a common orbiting spur gear andare disposed about the face of the housing.

In another aversion, the shafting has a pair of diametrally opposed, or180° out-of-phase eccentric surfaces upon each of which is mounted aseparate spur gear for rotation with respect thereto. The twoout-of-phase spur gears are constrained from rotation with respect thegearbox housing but orbit non-rotatably in engagement with a ring gearrotatably journalled on the housing. The orbital movement of the spurgears out-of-phase provides inherent dynamic balancing of the inertialforces of the orbiting spur gears. Power inputted to the ring gear, suchas by a wind turbine impeller hub provides a large speed increase to theshafting, which may have a power generator coupled to each opposite end.In one version, the shafting is a one-piece member with both eccentricsthereon. In another version or embodiment, the eccentrics for the spurgears are each on a separate half shaft. Alternatively, if the power isinputted to the shafting on either version the transmission operates asa speed reducer; however, torque multiplication is provided to the ringgear for increased torque output. A swash plate provides wear surfacesfor sliding contact of the spur gears in one direction normal to theaxis of rotation; and, the swash plate has wear surfaces for sliding onthe casing rods in a direction at right angles to the one direction forenabling the orbital non-rotating movement of the spur gears.

The speed/torque increaser of the present disclosure thus provides amechanism for driving in some versions a generator and a pair ofgenerators in other versions such as employed in a wind turbinegenerator and which is relatively small, lightweight and havingsimplified construction.

These and other non-limiting characteristics of the disclosure are moreparticularly disclosed below.

BRIEF DESCRIPTION OF THE DRAWINGS

The following is a brief description of the drawings, which arepresented for the purposes of illustrating the exemplary embodimentsdisclosed herein and not for the purposes of limiting the same.

FIG. 1 is a side view of a first exemplary embodiment of a speedincreaser of the present disclosure.

FIG. 2 is an exploded perspective view of the first exemplary embodimenta speed increaser of the present disclosure.

FIG. 3 is a series of different views of a second exemplary embodimentof a speed increaser of the present disclosure.

FIG. 4 is an exploded perspective view of the second exemplaryembodiment of a speed increaser of the present disclosure.

FIG. 5 a is an end view of another version of the speed increaser of thepresent disclosure.

FIG. 5 b is a cross section of the speed increaser of FIG. 5 a.

FIG. 6 is an exploded view of the speed increaser of FIG. 5.

FIG. 7 is an exploded view of the swash plate of the speed increaser ofFIG. 5.

FIG. 8 is a phantom pictorial view of the swash plate of FIG. 7illustrating the lubricant passages.

FIG. 9 is a side view of the version of FIG. 5 illustrating thelubricant supply and vent ports.

FIG. 10 is a view from the end of the output shaft of the speedincreaser of FIG. 9.

FIG. 11 is a cross-section of the speed increaser of FIG. 5 assembledwith an electric generator.

FIG. 12 is a view of the version of FIG. 11 incorporated in the hub of afluid turbine with portions of the housing broken away and mounted on asupport.

FIG. 13 is a cross-section of the impeller hub speed increaser andgenerator of FIG. 12.

FIG. 14 is an enlarged cross-section of the impeller hub speed increaserand generator of FIG. 13.

FIG. 15 is a perspective view of a version of the speed increaser of thepresent disclosure having multiple output shafts.

FIG. 16 is a cross-section taken along the section indicating lines16-16 of FIG. 15.

FIG. 17 is a section view taken along section indicating lines 17-17 ofFIG. 16.

FIG. 18 is a perspective view of another version of the speed increaserof the present disclosure from power inputted to the ring gear and poweroutputted to opposite ends of the shafting.

FIG. 19 is a front view of the speed increaser of FIG. 18.

FIG. 20 is a section view taken along section indicating lines 20-20 ofFIG. 19.

FIG. 21 is another perspective view sectioned along section indicatinglines 21-21 of FIG. 19.

FIG. 22 is an exploded view of the speed increaser of FIG. 18.

FIG. 23 is a perspective view f one of the spur gears of thetransmission of FIG. 18.

FIG. 24 is an enlarged perspective view of a portion of the gear of FIG.23.

FIG. 25 is an enlarged exploded view of a portion of FIG. 24.

FIG. 26 is a plan view of one of the swash plates of the transmission ofFIG. 18.

FIG. 27 is a front elevation view of FIG. 26.

FIG. 28 is a perspective view of the swash plate of FIG. 26.

FIG. 29 is an end view of the swash plate of FIG. 26.

FIG. 30 is a cross-sectional view of another version of the speedincreaser of the present disclosure installed in the propeller hub of awind turbine for driving dual power generators.

FIG. 31 is a section view of another version of the transmission of thepresent disclosure employed as a speed increaser for a driving dualpower generator from opposite ends of a one piece shaft.

FIG. 32 is an exploded view of the transmission of FIG. 31.

DETAILED DESCRIPTION

A more complete understanding of the components, processes andapparatuses disclosed herein can be obtained by reference to theaccompanying drawings. These figures are merely schematicrepresentations based on convenience and the ease of demonstrating thepresent disclosure, and are, therefore, not intended to indicaterelative size and dimensions of the devices or components thereof and/orto define or limit the scope of the exemplary embodiments.

Although specific terms are used in the following description for thesake of clarity, these terms are intended to refer only to theparticular structure of the embodiments selected for illustration in thedrawings, and are not intended to define or limit the scope of thedisclosure. In the drawings and the following description below, it isto be understood that like numeric designations refer to components oflike function.

Shown in FIGS. 1 and 2 is an exemplary embodiment of a speed increaserof the present disclosure. The speed increaser's input source and primemover, such as an electric motor, a hydraulic motor, or a wind turbineis capable of being mounted to a hub plate 11. The hub plate may beattached to an input shaft 25, as seen in FIG. 1, if desired. Thegearing arrangement is contained in a housing assembly 30 comprising ahousing member or gearbox housing 1. The input shaft 25 enters thehousing member 1 through a central opening 32 in a seal plate 7. Theoutput shaft 4 enters the housing member 1 through a central opening 34in a top plate 2. The seal plate and top plate are attached to thehousing member 1 by fasteners such as screws 21, 23.

An internal spur gear 10 is mounted to the hub plate 11. As the hubplate 11 rotates, the internal spur gear 10 is rotated.

An external spur gear 8 engages the internal spur gear 10. One or morebearings 16 may be inserted to separate the external spur gear 8 fromthe hub plate 11. The external spur gear 8 may include a bore 38 in itscenter (i.e. along the rotational axis). As shown here, a bearing 17 islocated within this bore. An eccentric ring 9 is located within thebearing 17 and an output shaft 4 engages the eccentric ring 9. In someembodiments, the output shaft 4 extends into a bore 40 located in thecenter of the hub plate 11.

The external spur gear 8 moves in an orbiting, non-rotating manner withrespect to the rotation of the internal spur gear 10. Put another way,the external spur gear 8 is sized so that it fits inside the internalspur gear 10, but is not so large that it meshes completely with theinternal spur gear. The center of the internal spur gear is offset fromthe center of the external spur gear by a distance known as the offsetdiameter. The eccentric ring 9 is shaped so that the output shaft 4 iscoaxial with the hub plate 11.

The non-rotation of the external spur gear 8 is enforced throughconnection to a cross plate 6. The cross plate 6 is located generallybetween the top plate 2 and the external spur gear 8. Two cross guidepins 5 are mounted in the external spur gear. As shown here, the twocross guide pins are equally spaced from the geometric center of theexternal spur gear and are located on opposite sides of a line, so thatthe two cross guide pins are located 180° apart from each other. Thepins extend from the external spur gear 8 into a first pair of elongatedslots 42 in the cross plate 6. The portion of the cross guide pins 5connected to the external spur gear 8 are round in cross-section, whilethe portion of the cross guide pins 5 extending into the slots of thecross plate 6 are square in cross-section. The slots confine the pinsand allow orbital motion of the spur gear 8.

Similarly, two cross guide pins are mounted in the top plate 2 usingfasteners 22. These pins extend from the top plate 2 into a second pairof elongated slots 44 in the cross plate. The portion of the cross guidepins 5 connected to the top plate 2 are round in cross-section, whilethe portion of the cross guide pins 5 extending into the slots of thecross plate 6 are square in cross-section. Again, the slots confine thepins and allow motion of the cross plate along only one axis. The firstpair 42 and second pair 44 of elongated slots are perpendicular to eachother. The combination of the pins extending from the top plate 2 to thecross plate 6, and the pins extending from the cross plate 6 to theexternal spur gear 8, prevent the external spur gear from rotating, butstill allow orbital motion.

As the internal spur gear 10 rotates, its teeth engage correspondingteeth on the external spur gear 8. The external spur gear has fewerteeth than the internal spur gear. As a result, the center axis of thenon-rotating external spur gear orbits faster than the internal spurgear. Due to this orbital motion of the external spur gear 8, theeccentric ring 9 rotates, causing the output shaft 4 to rotate as well.Again, the output shaft 4 is co-axial with the hub plate 11 due to thecombination of eccentricities in the external spur gear 8 and theeccentric ring 9.

Shown in FIGS. 3 and 4 are perspective views of another exemplaryembodiment of the speed increaser. The gearing components are arrangedbetween a hub plate 100 and a back plate 170. The hub plate 100 ismounted on a geared bearing 160. The hub plate 100 also transmits aninput rotational load to the geared bearing 160. The geared bearing 160has teeth on its inside face.

An inner gear 120 has teeth located on its outside face. The inner gear120 has fewer teeth than the geared bearing 160. The inner gear ispositioned inside, but not concentric with, the geared bearing 160 suchthat their gear teeth engage. The inner gear 120 moves in an orbiting,non-rotating manner with respect to the rotation of the geared bearing160. The inner gear 120 contains a bore 122 and has a bore axis which isoffset from the bore axis of the geared bearing 160 for a distance knownas the offset diameter.

A bearing 130 is located within the bore 122. Located within the bearing130 is an output assembly 140. The output assembly 140 comprises a ring142 and an output shaft 144. The ring 142 also contains an offsetdiameter, such that the output shaft 144 and the hub plate 100 areco-axial. The bearing 130 provides a rotational slipping motion betweenthe output shaft 144 and the bore 122 of the inner gear 120.

The ends of the output shaft 144 extend through bores in both the hubplate 100 and the back plate 170. The two ends are supported by two (2)sets of bearings 105.

The inner gear 120 is separated from the hub plate 100 by the thrustring 110, which is bolted to the hub plate 1. The geared bearing 160 isalso bolted or affixed to the hub plate 100, such that the thrust ringis within the geared bearing 160. The thrust ring 110 has a slightlysmaller diameter than the inner gear 120, to ensure that the thrust ringdoes not contact the teeth of the inner gear as the inner gear orbits.

A swash plate 150 separates the inner gear 120 from the back plate 170and fits within the diameter of the geared bearing 160. The swash plate150 also prevents the inner gear 120 from rotating. The swash plate 150is slotted on four quadrants to fit over the drive dogs. The drive dogsare square keys which mate with the slots on the swash plate 150. Two(2) of the drive dogs 172 are located on the back plate 170 and matewith slots 152. The other two (2) drive dogs 124 are located on theinner gear 120 and are rotated 90 degrees in orientation from the two(2) drive dogs 172 located on the back plate 170. Although the drivedogs 124, 172 are shown here as separate components, in this embodimentthey may be made as integral parts of the inner gear 120 and back plate170, respectively. The drive dogs 124 mate with slots 154 on the swashplate 150. This arrangement prevents the inner gear 120 from rotating,but allows the inner gear 120 to orbit.

The geared bearing 160 has a height such that the thrust ring 110, innergear 120, and swash plate 150 are all contained within it. Put anotherway, when assembled and seen from the exterior, the hub plate 100,geared bearing 160, and back plate 170 may be visible, but the thrustring 110, inner gear 120, and swash plate 150 need not be seen.

When a power source applies rotational force to the hub plate 100, thehub plate's bolted connection with the geared bearing 160 causes thegeared bearing to rotate with the same rotational force and at the samerotational speed. Because the teeth of the inner gear 120 are engagedwith the teeth of the geared bearing 160, the rotational forces on thegeared bearing are transferred through the inner gear 120 to the drivedogs and the swash plate 150. Because the drive dogs and swash platewill not allow the inner gear 120 to rotate, the rotational forces inthe geared bearing 160 act as a tooth separating force, pushing theinner gear in an orbiting motion around the output shaft 144. Theorbiting motion and transferred force causes the output shaft 144 torotate.

The resulting speed increaser has a gear ratio calculated by the numberof teeth in the geared bearing 8, divided by the difference in number ofteeth between the geared bearing 8, and the inner gear 2. The gear ratiomay be from about 20:1 to about 100:1 (output:input).

Referring to FIGS. 5 a, 5 b and 6, another embodiment or version of thepresent disclosure is indicated generally at 200 and includes a housing202 having a generally cylindrical wall portion 204 forming the outerperiphery thereof and having an inner hub 206 which has a bearingassembly therein indicated generally at 208 which has journalled thereinan output shaft 210. The shaft 210 has a raised diameter portion 212which is received in close fitting engagement with the inner race of thebearing 208. Shaft 210 has axially spaced from diameter 212 an eccentricdiameter 214 the amount of offset thereof which will be hereinafterdescribed.

The speed increaser 200 has an input shaft 216 with a flanged hub 218which is attached to a generally circular plate 220 extending radiallyoutwardly therefrom which plate is attached adjacent its outer peripheryto an internally toothed ring gear 222 by a plurality ofcircumferentially spaced fasteners such as cap screws 224. The ring gearis journalled on its outer periphery in a bearing indicated generally at226 which bearing has the outer race thereof denoted by referencenumeral 228 secured to a flange 230 formed on housing 202 by a pluralityof fasteners such as cap screws 232. Bearing assembly 226 preferablyincludes a plurality of ball races denoted by reference numeral 234 butmay alternatively comprise a plain bearing or other suitable bearing.

Shaft 210 has a diameter 236 formed on the end thereof which diameter isjournalled by a bearing assembly indicated generally at 238 in a centralbore 240 provided in the plate 220.

Thus, in operation, power inputted to shaft 216 causes plate 220 torotate ring gear 222 in bearing assembly 226.

An externally toothed spur gear 242 is disposed within ring gear 222;and, the gear 242 has a bearing assembly indicated generally at 244provided on the hub of gear 242 which bearing assembly has its innerrace assembled in closely fitting engagement over the eccentric diameter214 provided on the output shaft 210. The spur gear 242 has a pitchdiameter of its teeth slightly less than the pitch diameter of theinternal teeth on ring gear 222. It will be understood that the offsetor eccentricity of the diameter 214 is equal to the difference in thepitch diameter of the ring gear teeth and the pitch diameter of the spurgear teeth.

Housing 202 has a pair of elongated cross guide slots 244 formed thereinextending disposed in diametrally opposed radially extendingorientation, one of which pair 244 is shown in FIGS. 5 b and 6.

Spur gear 242 has a similar pair of diametrally opposed radiallyextending cross guide slots 246 formed therethrough, one of which isshown in FIG. 5 b and both of which are shown in FIG. 6. A swash plateindicated generally at 248 has a clearance hole 250 formed centrallytherein for clearing the hub 206 of the housing; and, the swash platehas a pair of diametrally opposed radially extending cross guideprojections in the form of dogs or lugs 254 provided on the end ofdistal face thereof in FIG. 6 or right-hand face thereof in FIG. 5 bwith one of the pair of dogs 254 shown in FIGS. 5 b and 6. The axiallyopposite face of the swash plate 248 or left-hand face in FIG. 5 b andproximal face in FIG. 6 has a second pair of cross guide projections inthe form of dogs or lugs 256 formed thereon in diametrally opposedrelationship with both of the second pair of dogs 256 illustrated inFIG. 6. The pair of cross guide projections or dogs 254 slidinglyengages the slots 244 in housing 202; and, the second pair of crossguide projections or dogs 256 slidingly engages the slots 246 in thespur gear 242. It will be understood that the pair of dogs 254 arediametrally arranged at 90° to the orientation of the dogs 256 to permitorbital movement of the spur gear 242.

Bearing assembly 208 is retained in the housing hub 206 by a collar 258secured to the housing by cap screws 260.

In the present practice, it has been found satisfactory to form theswash plate and dogs integrally of titanium or aluminum material. Theslots formed in the housing may have wear resisting inserts on thesliding surfaces thereof and formed of material with a pressure-velocityrating

${PV} = {\frac{{Applied}\mspace{14mu}{Force}\mspace{14mu}(N)}{{Projected}\mspace{14mu}{bearing}\mspace{14mu}{area}\mspace{14mu}\left( {m\; 2} \right)} \times {linear}\mspace{14mu}{velocity}\mspace{14mu}\left( {m\text{/}\sec} \right)}$of 275,000 125 KW unit. In the present practice, it has been foundsatisfactory to use a bronze alloy commercially available and sold underthe designation “ToughMet® 3 AT110 Temper Plate” and obtained from theBrush-Wellman Company, Toledo, Ohio. In the present practice, the outputshaft has been satisfactorily formed of titanium material; however,other suitable materials may be used. The orbital gear has beensatisfactorily formed of SAE 1050 carbon steel hardened to about 20 to24 on the Rockwell “C” scale; however, other suitable gear materials maybe employed. The slots in the spur gear also may have bronze alloyinsert plates (not shown) for providing wear resistance thereto.

Referring to FIG. 7, the swash plate 248 has the dogs 254 and 256provided with hardened face plates denoted 258 for dogs 254 and 259 fordogs 256. The face plates may be retained on the dogs by threadedfasteners such as countersunk screws 262. In the present practice, ithas been satisfactory to form the face plates on the dogs of AISI type440 stainless steel hardened to a range of about 50-55 on the Rockwell“C” scale. However, other suitable hardened materials may be used.Additional wear plates 257 are mounted on the faces of the swash plateadjacent the dogs 254, 256 to axial lash and reduce friction between theswash plate and the housing.

Referring to FIGS. 7 and 8, the swash plate dogs 254, 256 are shown ashaving a plurality of cross-bores shown shaded in FIG. 8 and denoted byreference numerals 254, 266 which are connected to opposite sides of thelugs and which intersect grooves 268 formed on the outer surface of theplates attached to the sides of the dogs. The cross-bores intersectgrooves such as 270, 272 formed in external plates 274, 276 provided onthe faces of the swash plate to provide continuous passages forlubricants. The cross-bores such as 264, 266 communicate with holes 267in the wear plates (See FIG. 7) and feed lubricant to the plate grooves268.

Referring to FIGS. 5 b, 9 and 10, inlet ports 277 are provided in thehousing and have supply fittings 278 attached thereto connected to arelatively high pressure lubricating system 281 adequate to provide afilm of lubricant between the sliding cross guide projections and theslots in the ring gear and housing. The housing also has vent ports 280provided therein. A lubricant face seal 279 is provided between thehousing and the sliding dogs 254.

Referring to FIG. 11, another embodiment of the speed increaser of thepresent disclosure is indicated generally at 300 and comprises the speedincreaser indicated generally at 302 integrated with an electricalgenerator indicated generally at 304 assembled in a common housing 306which has a plurality of generator stator windings 308 disposed on theinterior thereof. The housing has an end wall portion 310 which maycomprise a separate plate attached thereto by fasteners such as capscrew 312 and which has a central bearing assembly indicated generallyat 314 and which is retained by a retaining collar or plate 316 securedto the end plate 310 by suitable fasteners 318.

Bearing 314 has one end of the hollow output shaft 320 journalledtherein. The output shaft 320 has a rotor 322 mounted thereon forrotation therewith and which rotor includes generator magnets 324disposed for, upon rotation of shaft 320, generating current in thestator windings 308. The output shaft 320 extends continuously throughthe speed increaser 302 and has the opposite end thereof journalledtherein as will hereinafter be described.

Housing 306 has a radially inwardly extending flange portion 326 whichhas formed therein a pair of diametrally opposed radially extendingcross guide slots 328. Housing 306 also has a radially outwardlyextending flange 330 onto which is secured an outer bearing race ring332 by suitable fasteners, such as circumferentially spaced cap screws334. The outer bearing race 332 has journalled therein the outerperiphery of an internally toothed ring gear 336 for rotation onbearings 338 with respect to the outer race 332. The ring gear hassecurely attached thereto for rotation therewith an input member or hubplate 340 and retained thereon by suitable fasteners such as cap screws342. The input member 340 has a centrally disposed bearing assemblyindicated generally at 344 and into which is journalled the opposite endof output shaft 320 on the reduced diameter portion 346 thereof. It willbe understood that the input member is connected to a source of rotarypower such as the impeller of a fluid turbine or a hydraulicallyoperated motor.

An externally toothed orbital spur gear 348 is disposed within the ringgear 336 and is journalled about an eccentric diameter 350 on the outputshaft by a suitable bearing assembly indicated generally at 352. Thespur gear has a pair of diametrally opposite radially extending crossguide slots (not shown in FIG. 11) into which are received a pair ofcross guide dogs (not shown in FIG. 11) extending from an axial face ofa swash plate (not shown) having a pair of cross guide dogs 354extending into the slots 328 in the housing in a manner similar to thearrangement of the speed increaser of FIG. 5. The construction of thering gear and spur gear is similar to that of the version of the speedincreaser shown in FIG. 5. Rotation of the input member 340 causesrotation of the ring gear 336 which effects non-rotating orbiting of thespur gear 348 and driving of output shaft 320.

Referring to FIGS. 12, 13 and 14, another version of a combination speedincreaser and generator is indicated generally at 400 and includes agenerator assembly indicated generally at 402 which has the input member404 thereof attached on inward flange 405 of to the hub 406 of a fluidturbine impeller which has apertured attachment bosses such as boss 408formed thereon for securing fluid turbine blades (not shown) thereon.The hub 406 is received over the generator 402 and attached to an endring 410 which has an outer bearing race 412 secured thereto which isjournalled on an inner bearing race 414 attached to an end plate 416 ofthe housing for the generator 402.

The output shaft 418 has one end journalled in the end plate 416 by abearing assembly 420; and, the opposite end of shaft 418 is journalledby bearing assembly indicated generally at 422 for rotation with respectto the impeller of 406. It will be understood that the construction andoperation of the speed increaser indicated generally at 424 is otherwisesimilar to that of the versions of FIG. 11. The embodiment or version400 thus permits the speed reducer and generator to be housed completelywithin the impeller hub of a fluid turbine.

As shown in FIG. 13, the version 400 may be attached to a supporthousing such as housing 430 which may be rotatably mounted on a tower432. In the arrangement of the version 400, it will be understood thatthe impeller hub may contain servo-motors (not shown) for changing thepitch of the un-shown blades; and, therefore, the hollow tubular outputshaft 418, which extends the full length of the generator and speedincreaser, permits power leads to be supplied through the hollow outputshaft.

Thus, the speed increaser of the present disclosure is compact, andquite lightweight for a given power handling capacity.

Referring to FIGS. 15, 16 and 17, another version of the presenttransmission employed as a speed increaser of the present disclosure isindicated generally at 500 and includes a housing 502 with a radiallyoutwardly extending flange 504 which has attached thereto by suitablefastening means, for example, cap screws 506, an outer bearing race 508which has journalled on its inner periphery by suitable bearingsindicated generally at 510, the outer periphery of an internally toothedring gear 512. An input member in the form of a circular plate 514 isattached to the ring gear by suitable fasteners such as cap screws 516;and, the input member 514 has a central hub 518 which is adapted forconnection to a source of power as, for example, the impeller of a fluidturbine or hydraulic motor.

Disposed within the internally toothed ring gear 512 is an externallytoothed spur gear 520 which has a plurality of diametrally opposed slots522 formed therein into which are received cross guide dogs or lugs 524extending from a swash plate 526. Similar slots 528 are formed in thehousing 502, shown in dashed outline in FIG. 7, into which are receivedcross guide dogs or lugs 530. The slots 522 in the spur gear 520 aredisposed at right angles to the slots 528 in the housing.

The housing 502 has disposed thereabout in spaced arrangement aplurality of output shafts 532, each of which has an end thereofjournalled in a pair of bearings 534, 536 and extending outwardly of thehousing 502. The opposite end of each shaft 532 has an eccentric 540formed thereon which is journalled in bearings 538 provided in the spurgear 520. In operation, rotation of the input member 514 and ring gear512 effects orbiting of the spur gear 520 in a non-rotating mannerwithin ring gear 512 and effects rotary movement of each of the outputshafts 532. Thus, the embodiment 500 provides for multiple output shaftsdriven by a single input shaft utilizing a single non-rotating orbitingspur gear for effecting speed increasing of each of the multiple outputshafts 532. The embodiment 500 has particular application for connectionto fluid turbine generators such as wind generators in that smallercapacity generators may be driven by each of the output shafts enablingsome of the generators to be disabled while others remain operative,such as during high wind conditions.

In the present practice, an exemplary speed increaser and generatoraccording to the present disclosure with a power output of 120 KW has anoutput shaft with a diameter of about 76 mm, a ring gear pitch diameterof about 482 mm, a speed ratio of 80:1 and weighs about 585 lbs (265Kg), a speed increaser-generator with a power output of about 600 KW hasa ring gear pitch diameter of about 122 cm and an output shaft diameterof about 152 mm.

Referring to FIGS. 18 through 25, another version of the speed increaseris indicated generally at 600 and has an annular input member or poweredring 602 journalled for rotation on a housing indicated generally at 604which comprises symmetric half shells or casings 606, 608 each having anouter bearing race respectively 610, 612, each of which has a pluralityof circumferentially spaced bearings 616, 618 respectively against whichan inner axially extending flange portion 620 of ring 602 is journalled.The annular input member or powered ring 602 has a plurality of internalteeth 622 formed about the inner periphery thereof and thus comprises aring gear. In the present practice, for a 250 KW speed increaser, thecasings 606, 608 have an outer diameter of about 26″ (660 mm); and, theannular power input member or powered ring gear 602 has teeth with apitch diameter of about 19″ (482 mm).

Referring to FIGS. 20, 21 and 22, the speed increaser 600 has a first orleft-hand power output member in the form of half shaft 624 which isjournalled for rotation in housing 602 by a bearing assembly indicatedgenerally at 626, which is retained by a r flange 628 on the half shellor casing 606 such as, for example, by fasteners (not shown) receivedthrough holes 630 provided in the flange 628. The power output member624 has provided its inner end which extends through the casing bearing626, an eccentric surface 625. In the present practice, for a 250 KWspeed reducer, the power output shaft 624 has a diameter of about 3″ (76mm); and, the eccentric surface 632 has an eccentricity with respect toaxis rotation of shaft 624 of about ¼″ (6.4 mm).

A corresponding right-hand oppositely disposed power output member inthe form of a half shaft 632 is journalled for rotation about a commonaxis with half shaft 624 in a bearing assembly indicated generally at634 retained by a suitable flange 636 in the right-hand half shell orcasing 608. The portion of right-hand power output shaft 632 extendsinwardly of the housing 604 and casing 608 and has an eccentric surface638 provided thereon which has a similar eccentricity of about ¼″ (6.4mm) with half shaft 632 having a diameter similar to that of poweroutput shaft 624.

Casing 608 has a plurality of spaced recesses or pockets 640 formed onthe inner face thereof, as shown in FIG. 22; and, in the presentpractice four such recesses or pockets. The pockets 640 each havereceived therein and secured thereto one end of a support bar 642, whichbars extend through the annular ring gear 602 and other internalcomponents of the speed increaser as will hereinafter be described ingreater detail. The opposite end of each of the bars 642 is received ina corresponding pocket (not shown) in the remaining casing or half shell606 and secured therein for supporting the casing 606 on the casing 608.In the present practice, the bars 642 are secured in the pockets 640 inthe respective casing 606, 608 by unshown fasteners received throughholes such as holes 644 shown in casing 606 (see FIGS. 19, 22).

Referring to FIGS. 20-23, an orbiting non-rotating spur gear indicatedgenerally at 646 is journalled for rotation on eccentric surface 625 bya bearing assembly indicated generally at 648 and retained on the gearby retaining flange 650. Gear 646 has teeth thereon operative toorbitally engage teeth 622 of power input member 602. In the presentpractice it has been found satisfactory to provide clearance for thenon-engaging teeth of the orbiting gear 646 during its orbital movementby the following formula:

Units Operator Input External Gear - # of teeth Te (#) Internal Gear - #of teeth Ti (#) Pitch P (#) Pressure Angle φ1 (degrees) Addendum A (%)Calculated Gear Data Addendum Dimension Ad (inches) = (1/P) *A GearRatio GR (#):1 = Ti/(Ti − Te) External Outer Radius R01 (inches) =((Te/P)/2) + Ad Internal Ini Radius R1 (inches) = ((Ti/P)/2) − AdExternal Base Radius Rb1 (inches) = (Te/(2*P))*cos(radians(φ1)) InternalBase Radius Rb2 (inches) = (Ti/(2*P))*cos(radians(φ1)) Involute PressureAngle Inv. φ1 (degrees) = tan(φ1*0.01745) − (φ1*0.01745) Eccentricity C(inches) = (((Ti/P) − (Te/P))/2) E1 (degrees) = ((acos(radians(((R1*R1)− (R01*R01) − (C*C)))/(2*C*R01))/.0174532 E2 (degrees) = (Te/Ti)*E1 φt1(degrees) = ((asin((R01*(sin((E1*0.0174532925))))/R1)) − E2)/.0174532φ01 = ((acos((Rb1/R01))/.0174532 Inv. φ01 = tan(φ01*0.0174532) −(φ01*0.0174532) φ = (Te/Ti)*(Inv. φ01 − Inv. φ1) δ = ((Te/Ti)*(Inv. φ01− Inv. φ1) + Inv. φ1 X2 = δ − (φt1*0.01745) φ2 (degrees) =((acos(Rb2/R1))/.0174532 X1 = tan(φ2*0.0174532) − (φ2*0.0174532) GearTip Clearance CL (inches) = ((X2 − X1)*R1)*.001

Spur gear 646 is shown in greater detail in FIG. 23 as having a pair ofdiametrally oppositely disposed slots 652, 654 through which two of thebars 642 pass respectively and which have anti-friction padsrespectively 656, 657 provided therein.

A second non-rotating orbital spur gear indicated generally at 658 isjournalled for rotation on eccentric surface 638 by a bearing assemblyindicated generally at 660 retained on the spur gear 658 by a suitableretaining flange. In the present practice, gear 658 is identical to gear646 and oppositely disposed with respect thereto and also orbitallyengaging the teeth 622 of the powered input ring gear 602. Gear 658 hasoppositely disposed slots 664 (see FIG. 22) provided therethrough anddiametrally opposed.

At assembly, the power output shaft 624, 632 are assembled such that themaximum eccentricity of the surfaces 632, 638 are diametrally opposedsuch that the spur gears 646, 658 orbit 180° out-of-phase within ringgear 602.

Referring to FIGS. 24 and 25, the anti-friction wear pad installation isshown typically for the wear pads 656 for gear 646, however, it will beunderstood that the illustrations of FIGS. 24 and 25 is typical for wearpads of the slots for both gear 646 and gear 658.

Each of the anti-friction wear pads typically 656 has a sphericalsurface 666 on the back face thereof which is in contact with acorresponding concave spherical surface 668 provided in a mounting block670. One of the wear pads 666 has a lubricant port 672 for supplyinglubricant from the wear face thereof to the spherical surface 668. Thespherical surface 666 on the wear pad is sealed in the spherical recess668 by a suitable seal ring 676 such that lubricant only is fed throughthe spherical face of one of the pair of pads 656. The lubricant galleryfor the oppositely disposed pad 656 does not have a seal such that thepressure of the lubricant provides a force against only one of the padsfor taking up any lash and maintaining the pads in contact with thefriction surface of a swash plate lug to be hereinafter described. Theblock 670 has thrust bearing or face pads 678 accurately located on theblock 670 by pins 680 received therethrough and retained by a fastenersuch as bolt 681 engaging threads 682 in block 670.

Referring to FIGS. 20, 21, 22 and 26-29, the details of the swash platefor each of the spur gears 646, 658 are indicated generally at 669, 671respectively with plate 669 shown in greater detail in FIGS. 26-29; and,it will be understood that plate 671 is identical in construction withplate 669. The swash plates 669, 671 each have a central clearanceaperture denoted 673 in FIG. 28 for the shaft 624 and shaft 632 withrespect to plate 671. The plates 669, 671 each have a pair ofdiametrally oppositely disposed lugs extending from the axially innerface thereof as denoted for swash plate 669 by reference numerals 675and 677 in FIGS. 26-29. The tabs 675, 677 are received between the wearpads of the spur gear 646 with lug 675 extending between the wear pad656 and the lug 677 extending between the wear pad 657 (see FIG. 23) ofthe spur gear. It will be understood that the lugs 675, 677 extendfurther in a radial direction than the length of the wear pads such thatthe spur gear 646 can slide on the lugs 675, 677 in a direction along adiametral line connecting the two lugs.

The plates 669, 671 each have four rectangular apertures denoted 679,683, 685, 686 with respect to swash plate 669 in FIG. 26. It will beunderstood that similar lugs on plate 671 (not shown) are slidablyreceived in corresponding slots in the spur gear 658 with appropriatewear plates corresponding to wear plates 656, 657 for spur gear 646.

Each of the swash plates 669, 671 has a seal plate denoted by referencenumerals 687, 688 for swash plate 669, each of which has an aperturetherein which communicates with a collector recess such as 639, 641 (seeFIG. 22) formed on an inner face of the casing 608 for providinglubricant to the lugs of the plate 671. The seal plates 687, 690 forplate 669 each have a lubricant orifice therein denoted by 689, 690which, it will be understood, communicate with corresponding collectorrecess (not shown) formed on the inner face of casing 606. A seal (notshown) is disposed between recesses and pads 687, 688.

Referring to FIG. 20, lubricant passages 691, 692 are formed in the lugs675, 677 respectively for communicating with the apertures 689, 690respectively. Each of the lubricant passages 691, 692 in lugs 675, 677respectively has a cross port denoted 693, 694 respectivelycommunicating therewith for providing lubricant to the surface of thelug for sliding contact with the wear pads such as pads 656. The swashplate lug passages 691, 692 and cross passages 693, 694 typicallycommunicate with supply passages respectively 605, 607 provided incasing 606, which passages 605, 607 are connected to annular lubricantgallery such as 613 formed in the casing which communicates with asupply passage such as 617, 619. It will be understood that the lugs665, 667 on the swash plate 671 have similar lubricant passagearrangements as shown in FIG. 20.

Referring to FIGS. 26-29, each of the apertures 679, 685, 686, 683 hassupport flanges formed on two opposite sides thereof which flangesextend downwardly toward the lugs 675, 677 as denoted typically byreference numeral 695; and, these flanges provide support for wear padsas will hereinafter be described.

Referring to FIG. 21, each of the swash apertures 679, 685, 686, 683 ofswash plate 669 has one of the support bars 642 extending therethroughin sliding engagement in a direction at right angles to the slidingengagement of the lugs 675, 677. The bars 642 are in sliding contactwith wear pads typically denoted 696 and which are retained by blocks697. Each of the wear pads 696 has a spherical surface provided on thepad in contact with a corresponding concave spherical surface formed inthe respective block 697 therewith similar to the arrangementillustrated for pads 666, 668 in FIG. 24. Lubricant passages noted 698,699 are provided in the bars 642 which are in communication with supplyports such as ports provided in the recesses 639-641 of casing 608 asshown in FIG. 21. Thus, the swash plates 669, 671 slide in one directionon the bars 642; and, the spur gears 646, 658 slide with respect to theswash plate lugs in a direction at right angles to the movement of theswash plates on the bars 642. The bars 642, thus provide threefunctions, firstly to secure the half shells of the casings together,secondly to provide sliding registration for the swash plates andthirdly to provide a supply of lubricant to the wear pads for thesliding contact with the swash plates.

In the present practice it has been found satisfactory to form the wearpads for the swash plate support bars and lugs of bronze material; and,optionally, if desired, the surface of the wear pads may be coated witha material filled with polytetrafluoroethylene (PTFE) for enhancedanti-friction properties.

The speed/torque enhancing power transmission of the present disclosuremay be operated as a speed increaser by inputting power to the ring gear602 and providing power output through both of the half shafts 624, 632.Alternatively, the power transmission may be operated as a torqueenhancing transmission by inputting power to both half shafts 624, 632and providing enhanced torque output at reduced speed to the ring gear.In either of the afore said arrangements, the transmission of thepresent disclosure provides a relatively high numerical ratio of speedbetween the input and output by utilizing twin orbital spur gearsengaging a common ring gear with the spur gears orbiting in diametrallyopposed, or 180° out-of-phase, arrangement to provide inherent dynamicbalancing of the orbital movement. The arrangement of the powertransmission 600 thus enables substantial power transmission in aminimum of volume thereby permitting utilization of the transmissioninstallation which otherwise would require a prohibitively large powertransmission unit.

Referring to FIG. 30, another version of the speed increaser of thepresent disclosure is illustrated generally at 700 and has the speedincreaser 600 of FIG. 18 attached to a support housing 702 by fastenerssuch as bolts 704 threadedly engaging the casing 608 of the housing 604.Support housing 702 may be rotatably mounted to a stanchion or tower(not shown) for supporting a wind turbine. The annular power inputmember or ring gear 602 has its outer periphery attached to the hub 706of a wind turbine impeller, the hub having bosses with apertures such asaperture 708 provided circumferentially spaced thereabout for receivingimpeller blades (not shown). The hub may have a spinner or hub cover 711for providing streamlining thereof. The power output shaft 632 of speedincreaser 600 has a first power generator indicated generally at 710secured to the casing shell 606 of the speed increaser such as by aplurality of circumferentially spaced bolts 712. The power output shaft632 drivingly engages, such as for example by means of a key 714, therotor 716 of the power generator 710.

The oppositely disposed output shaft 624 of the speed increaser 600 hasengaged therewith in driving engagement by a suitable drive couplingsuch as, for example, key 718 the rotor 720 of a second generatorindicated generally at 722 which has its stator 724 attached to thecasing 608 by suitable means such as bolts 726 spaced circumferentiallythereabout. The stator 724 has stator coil 728; and, the rotor istypically provided with magnetic members 730. The embodiment 700 of FIG.26 thus enables the disposition of dual generators within the impellerhub and housing of a wind turbine for reduced volume and mass yetproviding the required speed increase from the impeller necessary todrive the generators and provide double the power output.

In the dual generator wind turbine arrangement 700 of FIG. 26, theoutput shafts 632, 624 are hollow and permit a stationary tube 728 to bedisposed therethrough so as to permit the electrical leads (not shown)from generator 710 to pass through the speed increaser 600 and thegenerator 722 for external connection through an unshown port providedin housing 702.

Referring to FIGS. 31 and 32, another version of the speed/torqueenhancing power transmission of the present disclosure is illustratedwherein a common ring gear 802 with internal teeth 804 is journalled forrotation via bearings indicated generally at 806, 808 on housingstructure comprising casings 810, 812 which are secured together by fourinternal bars denoted typically at 814, three of which are illustratedin FIG. 32.

A one-piece shaft 816 is journalled in casing 812 at one end by bearingassembly indicated generally at 818 and the shaft is journalled at itsopposite end in casing 810 by a bearing assembly indicated generally at820. It will be understood that bars 814 are secured at their oppositeends respectively to casings 810, 812. The output shaft 816 has a firstand second axially adjacent eccentric surface 822, 824 which are offsetdiametrally opposite or in other words, 180° out-of-phase on the shaft.The eccentric surface 822 has rotatably mounted thereon a spur gear 826;and, eccentric surface 824 has rotatably mounted thereon a second spurgear indicated generally at 828. Spur gears 826, 828 are constrained aswill hereinafter be described for non-rotatable orbital movement withthe teeth of each in engagement with the teeth 804 of ring gear 802 toprovide speed increase. Upon power input to and rotation of the ringgear 802 it causes orbital movement of the spur gears 826, 828 about theeccentrics 822, 824 and an increased speed of rotation of the shaft 816.The shaft 816 may have a hollow interior 830 as shown in FIG. 31 ifdesired for passage of electrical leads therethrough.

The spur gear 826 has diametrally opposed slots formed therein intowhich are received lugs such as lug 832 on a first swash plate 834 whichpermits the spur gear 826 to move along a vertical axis with respect tothe swash plate. The swash plate is slidably received on rods 814passing through the apertures in the spur gear 826 and swash plate 834to permit sliding movement of the swash plate 834 on rods 814 andpreventing rotation about the shaft axis of either the swash plate orthe spur gear. Sets of wear pads denoted typically at 836 are providedfor contact between the swash plate and the bars 814. Similarly, wearpads (not shown) are provided for sliding movement of the spur gear onlugs such as 832.

The second spur gear 828 is similarly disposed for sliding movement on apair of lugs 840 provided on the second swash plate 842 which hasapertures through which the rods 814 pass for enabling sliding movementof the swash plate on the bars 814 and casing 812 in a horizontaldirection or direction at right angles to the sliding movement of spurgear 828 on the lugs 840. The spur gear 828 is thus constrained fromrotation yet permitted to orbit in contact with the teeth 804 of ringgear 802 and rotatably on eccentric 824. Wear pads denoted typically byreference numeral 844 are provided on each swash plate 842 to preventrotation of the swash plate and spur gear but permits sliding movementof the swash plate on the bars 814. The embodiment 800 of FIGS. 31 and32 operates in the same manner as the embodiment 600; whereas, theembodiment 800 employs a one-piece shaft.

The speed/torque enhancing power transmission of the present disclosurethus provides for substantially relatively high power transmission anddoes so in a significantly reduced volume for the gear box and enableseither power input through a ring gear and power output through the endsof shafting which may either be a one-piece or separate half shafts forapplications requiring a speed increase at the output. Alternatively, ifpower is inputted through the opposite ends of the shafting, a highdegree of torque multiplication application can be outputted on the ringgear. The significant difference between the speed of rotation of thering gear and the shafting is accomplished by a pair of diametrallyopposed or 180° out-of-phase orbiting spur gears engaging the ring gearwhereby the spur gears are rotatably mounted on individual eccentricsprovided on the shafting. The speed/torque enhancing power transmissionof the present disclosure is described as installed in the power hub ofa wind turbine for driving a separate power generator on each of theopposite ends of the shaft thereby providing twice the power outputwithout increasing the size of the power transmission. While particularembodiments have been described, alternatives, modifications,variations, improvements, and substantial equivalents that are or may bepresently unforeseen may arise to applicants or others skilled in theart. Accordingly, the appended claims as filed and as they may beamended are intended to embrace all such alternatives, modificationsvariations, improvements, and substantial equivalents.

The invention claimed is:
 1. A speed/torque enhancing power transmissioncomprising: a) a housing structure; b) a ring gear member journalled onthe housing structure for rotation about an axis and adapted forexternal connection thereto for power transmission; c) a shaftingstructure journalled on the housing for rotation about said axis, saidshafting extending axially in opposite directions from the ring gearmember along said axis and having a first eccentric surface thereon anda second eccentric surface diametrally opposed to and axially adjacentsaid first eccentric surface; d) a first spur gear member disposed forrotatably contacting said first eccentric surface, and disposed on saidhousing structure for non-rotatable orbital movement about said axis fororbitally engaging the ring gear; e) a second spur gear member disposedfor rotatably contacting said second eccentric surface and disposed onsaid housing structure for non-rotatable orbital movement about saidaxis for orbitally engaging the ring gear; and, f) wherein upon powerinput to one of the ring gear and the shafting, the speed of the otheris respectively increased and decreased; and, further comprising: g) afirst plate member with a first set of surfaces disposed on oppositesides of said axis and contacting said first spur gear for slidingmovement in a first direction normal to said axis of rotation, with asecond set of surfaces on opposite sides of said axis contacting saidfirst spur gear for sliding movement in a second direction normal tosaid axis of rotation and orthogonal to said first direction; and h) asecond annular plate member with a first set of surfaces disposed onopposite sides of said axis and contacting said second spur gear forsliding movement in a first direction normal to said axis, with a secondset of surfaces on opposite sides of said axis contacting said secondspur gear for sliding movement in a second direction normal to said axisand orthogonal to said first direction.
 2. The transmission of claim 1,wherein said shafting structure includes a first half shaft with saidfirst eccentric surface thereon and a second half shaft with said secondeccentric surface thereon.
 3. The power transmission of claim 1, whereinsaid first and second spur gears are each disposed on said housingstructure for sliding movement along a first and second orthogonal axiswhich axes are normal to said axis of rotation.
 4. The powertransmission of claim 1, wherein said first and second sets of surfacesincludes removable wear pads.
 5. The power transmission of claim 4,wherein said wear pads include substantially spherically radiusedsurfaces contacting said plate.
 6. The power transmission of claim 5,wherein said spherically radiused surface includes an annular seal. 7.The power transmission of claim 6, further comprising a supply port forsupplying lubricant to the spherically radiused surface.
 8. The powertransmission of claim 1, wherein said housing structure includes aplurality of elongated axially extending guide members disposed incircumferentially spaced arrangement about the axis of rotation, saidmembers extending through said first and second spur gears in slidingcontact therewith, said guide members having opposite ends thereofsecured to said housing structure on axially opposite sides of said ringgear.
 9. The power transmission of claim 8, wherein said first andsecond spur gear each includes a set of removable wear pads forcontacting one of said guide members.
 10. The power transmission ofclaim 9, wherein said wear pads includes a spherical surface.
 11. Thepower transmission of claim 8, wherein each of said guide membersincludes a lubricant passage for supplying lubricant for said slidingcontact.
 12. The power transmission of claim 1, wherein said shaftingincludes a one piece shaft member extending through said ring gear. 13.The power transmission of claim 1, wherein the speed ratio of output toinput is in the range of about 38-50:1.
 14. The power transmission ofclaim 1, wherein the speed ratio of output to input is about 38:1 for a125 kilowatt power output.
 15. The power transmission of claim 1,wherein the speed ratio of output to input is about 50:1 for a 250kilowatt power output.
 16. The power transmission of claim 1, whereinthe speed ratio of output to input is in the range of about 38-50:1 uponpower input to said ring gear.
 17. The power transmission of claim 1,wherein the speed ratio of output to input for power input to the ringgear is about 38:1 for 125 kilowatt output and about 50:1 for 250kilowatt output.
 18. The speed enhancer of claim 1, wherein upon powerinput to the shafting structure the speed ratio of input to output is inthe range of about 38-50:1.
 19. A speed/torque enhancing powertransmission comprising: a) a housing structure; b) a ring gear memberjournalled on the housing structure for rotation about an axis andadapted for external connection thereto for power transmission; c) ashafting structure journalled on the housing for rotation about saidaxis, said shafting extending axially in opposite directions from thering gear member along said axis and having a first eccentric surfacethereon and a second eccentric surface diametrally opposed to andaxially adjacent said first eccentric surface; d) a first spur gearmember disposed for rotatably contacting said first eccentric surface,and disposed on said housing structure for non-rotatable orbitalmovement about said axis for orbitally engaging the ring gear; e) asecond spur gear member disposed for rotatably contacting said secondeccentric surface and disposed on said housing structure fornon-rotatable orbital movement about said axis for orbitally engagingthe ring gear; and, f) wherein upon power input to one of the ring gearand the shafting, the speed of the other is respectively increased anddecreased, wherein said housing structure includes a first and secondset of diametrally opposed surfaces disposed for sliding contact witheach of said first and second spur gear, said sliding surfaces includelubricant galleries for supplying pressurized lubricant thereto.